Indexing mechanism



Aug. 10, 1948. J. H. BARNES INDEXING MECHANISM Original Filed June 9. 1941 9 Sheets-Sheet 1 Z IN VENTOR. ames/160mm ATTORNEYS.

Aug. 10, 1948. J. H. BARNES INDEXING MECHANISM 9 Sheets-Sheet 5 Original Filed June 9, 1941 Aug. W, 1948. .1. H. BARNES INDEXING MECHANISM 9 Sheets-Sheet 4 Original Filed June 9, 1941 INVENTOR. JOM mbf flame;

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INDEXING MECHANISM Original Filed June 9, 1941 9 Sheets-Shec 5 INVENTOR.

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ATTORNEYS.

-9 Sheets-Sheet 6 J. H. BARNES I NDEXING MECHAN I SM Aug. 10, 1948.

Original Filed June 9, 1941 INVENTOR. ames 7 50mm ATToRNEYfi.

Aug. 10, 1948. J. H. BARNES INDEXING MECHANISM 9 Sheets-Sheet 7 Original Filed June 9, 1941 RNEYS.

INVENTOR. qm5 H. 54

75UWLM X ATTO Aug. 19, 1948.

J. H. BARNES INDEXING MECHANISM 9 Sheets-Sheet 8 Original Filed June 9, 1941 INVENTOR. \J mes l7. Bar/7P5 3 ATTORNEYS.

BY 2 E 1948- J. H. BARNES 2,446,865

INDEXING MECHANISM Original Filed June 9, 1941 9 Sheets-Sheet 9 INVENTOR.

75mm, I iz 3 ATTORNEYS.

Patented Aug. 10, 1948 INDEXING MECHANISM James H. Barnes, Glendale, Calif.

Original application June 9, 1941, Serial No. 397,171, now Patent No. 2,423,286, dated July 1, 1947. Divided 1944, Serial No. 542,767

8 Claims.

This invention relates to a profile generating mechanism and is particularly Well adapted for generating the profiles of the teeth of gears and similar rolling power transmitting elements.

It is the object of this invention to produce a profile generating mechanism which will produce a rollin power transmitting element, such as a gear, of greater accuracy than heretofore possible. The greater accuracy in the generation of the profile in the gear tooth results in quieter operation of the gears.

Another object of this invention is to produce a profile generating mechanism for rolling power transmitting elements which is highly flexible and which can generate or shape any profile desired where the profile is generated from a continuous curved 'evolute.

This invention also contemplates a profile generating mechanism which is universal in application because with the same tool it can generate or shape a gear or other rolling power transmitting element of any pitch.

Another feature of the invention is that it utilizes a simple tool, such as a simple cutting or shaping tool, which will generate gear teeth from any base circle diameter within the range of the machine elements.

The machine is useful in generating the profiles of all types of rolling power transmitting elements such as spur, helical, herring-bone, internal, and bevel gears as well as an infinite variety of toothed elements.

The machine is useful in generating convex as wall as concave profiles or surfaces and all types of involute curved surfaces including the circular involute curved surface. This machine will generate any desired precise form of involute curve and the same tool will cut gears of any pitch or pressure angle within the range of the machine.

In the drawings:

Fig. 1 is a front elevation of the machine.

Fig. 2 is a vertical section along the line 22 of Fig. 1.

Fig. 3 is a rear elevation of the machine along the line 33 of Fig. 2.

Fig. 4 is a vertical section along the line 44 of Fig. 2.

Fig. 5 is a horizontal section along the line 5-5 of Fig. 11.

Figs. 6, 7 and 8 are sections along the lines 66, 1-1 and 88 of Fig. 1.

Fig. 9 is a section along the line 9-9 of Fig. '1.

Figs. 10, 11, 12, 13, 15 and 18 are sections along the lines III-I0, III I, I2--I2, I3-I3, I5--I5, and I8-I8 of Fig. 1.

and this application June 29,

2 Fig. 14 is a section along the line I4-I4 of Fig. 4.

shaving,

comprises an electric motor Fig. 16 is a front elevation of a portion of the machine showing the cutting tool and its control elements in non-cutting position.

Fig. 17 is a front elevation similar to Fig. 1 6 but showing the cutting tool and its control elements at the end of the cutting or shaving stroke.

Fig. 19 is a detail showing a roughed out gear which is being cut and the path traversed by the cutting tool.

Referring more particularly to the drawings, the frame of the machine is designated I. The frame has journalled therein a shaft 2. One end of the shaft 2 is provided with a spindle 3 which serves as a work holder. This machine is adapted to generate the profiles of an infinite variety of power transmitting bodies. As herein shown by way of description rather than limitation, the work is shown as a gear 4 having helical gear teeth 5. Gear 4 is securely fixed upon spindle 3 by means of a washer 6 which rests against shoulder 1 on the spindle arbor 8, washers 9 and nut l 0.

During the profile enerating operation, which may be any shaping operation such as cutting, grinding or filing, the gear 4 is held stationary. Between these operations, however, the work is indexed or rotated to present a new tooth to the profile generating tool. This index-v ing mechanism, Figs. 2 and 3, comprises a cam gear I I which is journalled upon shaft I2 integral with frame I. The drive for the cam gear II I3 which drives pulley by means of belt I5. Pulley I4 is fixed upon shaft I6 which is journalled in the frame I. Gear I1, fixed on one end of shaft It, meshes with gear |8 fixed upon shaft I9. Shaft I9 is journalled in frame I. Gear 20, fixed on the other end of shaft I9, meshes with gear 2I fixed on shaft 22 also journalled in the frame I. Gear 23 fixed on shaft 22 meshes directly with cam gear II. The drive is as follows: Driven pulley I4 drives shaft I6 and gear l1. Gear I1 drives gear I8, shaft I9 and gear 2|]. Gear 20 drives gear 2|, shaft 22 and gear 23. Gear 23 drives cam gear II. Gear 20 also drives crank disk gear 24 for purposes described below.

The mechanism for holding the gear 4 in any position to which it is indexed comprises a circular rack 25 which is splined on to shaft 2, a driv ing gear 26 fixed to the face of rack 25 and a pawl 21 slidably mounted in housing 28 fixed to the frame I. Pawl 21 is backed up by compression springs 29 which tend to project pawl 21 toward the right and into engagement with rack 25.

Pawl 21 is provided on its inner face with a. roller 30 which rolls against cam face 3| of cam groove 32 formed in gear II. It will be noted that surface 3| of cam groove has a raised area 33. The raised area 33 has a greater radius than the rest of the cam surface 3| and therefore causes roller 30 to move radially outwardly from shaft 2 thereby withdrawing pawl 2! from interengagement with toothed rack 25. While the pawl 21 is disengaged from rack 25, shaft 2 and work gear 4 are free to be indexed.

The indexing of the gear 4 is effected by the following members: slide 35 supported for vertical sliding movement on frame i and provided I with a roller 36 which travels in cam groove 31. A lever 38 pivotally mountedon pin 3911s pivotally connected at one end with slide 35 and at the other end with connecting rod 4!]. Connecting rod 40 is pivotally connected as at M with slide member 42 slidably mounted in guide members 43 for vertical reciprocation. Slide 42 alsosupports drive pawl 44 for horizontal reciprocation.

One end of a bell crank 45, pivoted as at 46, has a pin and roller thereon operating in a vertical slot 41 in pawl 44 and a roller 48 on the other end of the bell crank rolls along cam face 50 of cam gear II. When pawl 2'! is disengaged from rack 25, as roller 30 rolls along surface 33, roller 36 rolls along the portion of cam groove 31 having the lesser diameter thereby causing slide 35 to travel downwardly, lever 38 to swing counterclockwise, and slide 42 to travel upwardly in guides 43. Just prior to the time that slide 42 begins to travel upwardly, roller 48 rolls upon the high side, that is, the portion of cam surface 50 having the greater diameter which swings bell crank 45 counterclockwise and shifts pawl 44 to the left to engagement with gear 26. Thus, as slide 42 slides upwardly it also raises pawl 44 thereby rotating gear 26 counterclockwise, Fig. 3, and indexes gear 4, Fig. l, clockwise to present the next tooth or surface to the profile generating tool.

It should be noted that pivot pin 39 which supports lever 38 is adjustable along its support and that the pivotal connection '52 between slide 35 and lever 38 is also horizontally adjustable. By shifting pivot 39 in slot 53 of support 5I to the left, Fig. 3. one can increase the stroke of pawl 44 and thereby increase the angular distance that the gear 4 is indexed. By shifting pivot 39 to the right, Fig. 3, the angular distance that gear 4 is indexed with each stroke of pawl 44 is decreased.

The profile generating tool can be any of the well known shaping tools such as acutting tool or grinding tool. By way of illustration, the profile generating tool is shown as a simple cutter 60 held in a tool holder 6I by set screws 62. The shaving tool holder BI is mounted on a tool holder slide 63. Slide 63 is slidably mounted on pivoted arm 64 by guides 65. Slide block 63 reciprocates radially of arm 64. This radial reciprocation is effected by cam 66. Cam 66 is pivotally supported upon a plate 70 by an Allen screw 61, bushing 68 and nut 69. Plate is slidably adjustable laterally in the horizontal groove II in the frame member I Figs. 7 and 9. Cam member 66 can also be adjusted by rotating the same about bushing 68. The bolts I2 and I3 at the top and bottom of cam 66 pass through elongated arcuate slots I4 in the cam 66 which permit limited pivoted 0r rotary adjustment of the cam 66.

Tool slide 63 is provided with a pin which supports roller 16 in cam groove of cam 66. As the arm 64 swings downwardly, roller I6 rolls against side wall 11 of the cam groove of cam 66 and causes tool slide 63 to slide radially inwardly along guideway 65 toward the gear from the position shown in Fig. 16 to that shown in Fig. 17-. As the arm 64 swings from the position shown in Fig. 17 upwardly to that shown in Fig. 16, the roller 76 engages the other side wall T8 of the cam groove of cam 66 which causes the tool slide to move radially outwardly of arm 64. Roller I6 has a snug fit in cam groove of cam 66.

Arm 64 has a circular ring portion 80 which is journalled on a circular bearing 8| secured to slide member 82 by screws 83. Slide member 82 is guided for horizontal reciprocation on the frame I by guideways 84 and 85. Slide member 82 and bearing member 8I are provided with an opening 86 for the shaft 2. 7 Thus, opening 86 provides a clearance as slide 82 and bearing 8| reciprocate laterally or horizontally with respect to shaft 2. The center of bearing 8|, that is, the center about which arm 64 pivots, is designated 90, Fig. 1. This center, of course, reciprocates laterally with bearing 8I.

Oscillation of the arm 64 about bearing 8| is effected by a lever 91 pivoted on shaft 2. A connecting rod 93 connects arm 9| with crank disk gear 24. Thus, rotation of crank gear 24 acting through connecting rod 93 oscillates arm SI about its bearing support 2. Arm BI is connected with the outer end of arm 64 by a slide connection 94 (Figs. 11, 15). Slide connection 94 comprises a slide member 55 secured to the end of arm Si by bolt 86. Slide member 95 has a sliding fit in guide member 81 bolted to the end of arm 64. Sliding connection 94 between driving arm HI and arm 64 is essential because arm 9I oscillates about a fixed center whereas arm 64 oscillates about center 8i which reciprocates in a rectilinear horizontal path with block 82.

Horizontal reciprocation of slide member 82 and bearing BI is effected by cam I00. Cam I00 is pivotally mounted by means of pin IflI upon plate I82. Plate I62 is slidably mounted upon frame I for lateral or horizontal adjustment. Plate I02 is provided with horizontal ribs I 63 which engage in horizontal grooves I64 in frame I, Figure 6. The cam slide base I92 can be clamped in any position of lateral adjustment by clamps I 65 which are secured by screws I06 to the frame I, Fig. 6. Screws I06 screw into openings I'll'I provided in frame I. The cam Inc can also be pivotally adjusted about pin IQI and secured in place by bolts I08 which pass through elongated angular slots H39 in the cam I 08. Pivoted arm 64 is provided with adjustable support member lit] for roller III which rolls in the cam groove of cam I00. Support IIO is adjustably supported in groove N2 of arm 64 by screws II3. Screws II3 pass through elongated slots H4 in support IIIl.

As shown in Fig. 16, the arm 64 is at the beginning of its clockwise stroke. As roller III travels upwardl in cam IOII the roller contacts wall II5 of cam I 00 which causes slide block 82 to slide or travel toward the left from the position shown in Fig. 16 to that shown in Fig. 17. On the reverse rotation of arm 64, roller III rolls along wall II6 of cam I60 and causes the slide 82 to travel progressively toward the right in guideways 84 from the position shown in Fig. 16 to that shown in Fig. 17. A hand operated locating arm I20 is pivoted to the frame at I2I and has a locating tooth I22 for interengaging gear 4 to locate the same preparatory to shaving the same to size, Figs. 16, 17.

The lower end of connecting rod 93 is supported on crank gear 24 by means of a pin and block I40. Block I40 is adjustable radially in guideways I4I of the gear 24 to vary its stroke. The upper end of connecting rod 93 is adjustably supported on arm 9|. Connecting rod 93 is pivotally supported on block I42 which is adjustable vertically in plate I43 by means of adjusting screw I44, Fig. 14. Plate I43 can be adjusted radially of arm 9| by loosening bolts i45 which are then free to slide in slot I46 in arm The gear 4 which may be a cast gear of metal, plastic, or any other material, may have its teeth roughed out. The gear which is to have its teeth shaped to the desired profile is mounted upon its support spindle 3 and properly located b locator I22 before being clamped into place by turning down nut I0. Locator I22 is now swung down to released position and the machine is set in operation. As arm 54 pivots downwardly clockwise about center 90, cam I00 acting through roller III shifts slide block 82 and the center of rotation 90 of arm 64 to the left, Fig. 16, along a straight line path determined by guideways 84. Simultaneously roller 16, operating in cam 645, causes the tool support and the tool to slide radially of arm 64 toward the center or rotation of the arm. It is this triple or compound movement to which th tool is subjected which determines the path of the tool and the surface which is generated by the cutting edge I30 of the tool 60. The path of the cutting tool 60 is shown in Fig. 19.

During the cutting operation the gear is held stationary by pawl 27 and rack 25. As the tool retreats from the work, that is, travels from Fig. 17 to Fig. 16, the indexing mechanism comes into play as above described and indexes or rotates the gear 4 one tooth so that the next tooth is now presented to the cutter 60. As shown, the tool is cutting the lower face of the gear teeth 5. After the lower face of the gear teeth have been shaved or cut to the proper profile, the gear is then turned around on the gear holder 3 which now presents the other face of the teeth to the cutting tool to have the proper profile generated.

It is evident that the profile generated by the cutting edge I30 of the tool can be adjusted to cut an infinite variety of profiles by adjusting the position of cams I00 and 66, as above described, by adjusting the angular oscillation of arm 64 which is accomplished by adjusting the pivotal connection of connecting rod 93 with crank gear 24 and arm 2|.

Referring to Fig. 19, as the tool moves from the dotted line position to the full line position, the axis 90, about which tool and arm 64 pivot, moves a distance equal to the distance from the position where the involute tangent (dotted line showing of tool) intersects the intersect line to the profile origin. This movement is efiected by cam I00. While the tool moves from a point on the profile of the tooth to the profile origin point, the distance of the tool edge I30 from the spindle 3 (center of gear 4) has decreased from a distance greater than to a distance equal to the radius of the base circle. This change in the position of the tool is effected by the cam 66 and the swinging arm 64. As herein shown, the evolute is a circle called the base circle and the involute is a circular involute curve. The evolute is shown as a circular curve for descriptive purposes only. The evolute can be any continuous curve, e. g., an elliptical, parabolic, or hyperbolic curve.

This application is a division of my copending application Serial No. 397,171, filed June 9, 1941,

6: and now Patent No. 2,423,286, granted July 1;

I claim:

1. In a machine for shaving a rolling power transmitting body while the body is held station-.- ary, comprising a shaft adapted to have mounted thereon the power transmitting body in non-rotative relation with said shaft, circular toothed means fixed on said shaft, a pawl adapted to interengage said circulartoothed means for locking the shaft while the said body is being shaved, a second pawl adapted to intermittently interengage and index said circular toothed member and shaft to present a new surface of the said body into gear shaving position, a plurality of rotary cams mounted concentrically with said shaft, said cams being arranged for unidirectional and simultaneous rotation, and means actuated by said cams and cooperating with said shaft and second pawl for projecting the first pawl into looking position when the second pawl is retracted and for retracting the first pawl as the second pawl moves into indexing relation with said circular toothed means.

2. The combination as set forth in claim 1 including a rotary cam arranged to retract said first pawl preparatory to the indexing step of said second pawl.

3. The combination as set forth in claim 1' including a rotary cam arranged to retract said first pawl preparatory to the indexing step of said second pawl, and resilient means for projecting said first pawl into interengagement with said circular toothed means when released by said cam.

4. The combination as set forth in claim 1 including rotary cam controlled means for projecting said second pawl into engagement with said circular toothed means and. for moving said second pawl tangentially of said circular toothed means to rotate the same while said first pawl is retracted.

5. In a machine for shaving a rolling power transmitting body, a shaft adapted to have mounted thereon the power transmitting body in non-rotative relation therewith, gear means fixed on said shaft for rotation therewith, a locking pawl and an indexing pawl adapted to be alternately projected into interengagement with said gear means for rotating said gear means with a step by step motion and for locking the same in a stationary position between said step by step movements, a rotary cam mounted concentric with said shaft and for retracting said locking pawl out of interengagement with said gear means while the indexing pawl is indexing said gear means, and rotary cam controlled means for projecting said indexing pawl into interengagement with said gear means and for rotating the same intermittently while said locking pawl i-s disengaged from said gear means, said cams being arranged for unidirectional and simultaneous rotation.

6. The combination as set forth in claim 5 wherein each of said pawls is controlled by separate cam ways joined together and arranged to rotate unidirectionally as a unit.

7. In a machine for shaving a rolling power transmitting body while the same is held stationary, a shaft adapted to have mounted thereon the power transmitting body in non-rotative relation therewith, circular toothed means mounted on said shaft for rotation therewith, a locking pawl and an indexing pawl adapted to intermittently interengage said circular toothed means, a rotary cam mounted concentric of said shaft and operatively connected to said locking pawl for controlling the same whereby the lockme; nail interengages. said. circular toothed number while the indexing pawl is disengaged, a rotary cam mounted eoiicentric of said shaft and for controtling the incitement of said. indexinc" pawl into. interengagex flent. with said circu- Iar toothed member prepaijhtory to rotating the same, and a notary cam fo l,- controll-ing the. tan- Zential movement; oi said infield-mg pawl while the same is inter-engaged with aid circular toothed member and while the loc g pawl is; retracted, the said three rotary cam members rotating as innit and always in the. seine direction.

8; The combination as set forth in claim '1 ineluding means tor valuing the tangential reciprocation of said: indexim pawl to: thereby vary the angular distance. that. the eiisenlar toothed. memher is indexed on each stroke of the indexing pawl.

JAMES H. BARNES.

REFERENCES CITED,

The tel-lowing references are of record in the file of this patent:

UNITED STATES PATENTS 

